Method of operation and regulation of thermal power plants



Sept- 2, 1952 v. H. PAvLEcKA ET Al.

METHOD OF' OPERATION AND REGULATION OF' THERMAL POWER PLANTS 2 SHEETS-SHEET l Filed 0017. 7, 1944 /N VEN TORS Sept. 2, 1952 v. H. PAvLEcKA ErAL 2,608,822

METHOD oF OPERATION AND REGULATION oF THERMAL PowER PLANTS Filed oct. 7, 1944 2 sl-xEETs-SHEET 2 AuToMATlcALLY v' v v ,8, AuToMATlcAI. LY

OPERATED VALVES OPERATED VALVES Patented Sept. 2, 1952 IWETHOD. OF OPERATION AND REGULATION OF'THERMAL POWER PLANTS Vladimir Pavlecka, Pacific Palisades, andFrederick Dallenbach, Inglewood, Calif., assignorsto Turbolectric Corporation,

Beverly Hills, y

Calif., a corporation of California Application October 7, 1944', Serial No. 557,654

11 Claims. l

This inventionY relates to` gas turbinev -power plants, and more particularly to the method of operation of such plantsY atY substantially constant temperature irrespective of load; variations, whereby. the. thermal eiiciency of the. plant is maintained constant. The invention also relates to, a. novel method vof starting power plants of the abovev type.`

The. subject of this invention is a basic improvementV in the application of theA simple Joule thermodynamic cycle, also known as the Brayton cycle, to the continuous combustion gas turbines.

The Joule cycle, operating at substantially constant pressure during combustion, is not well adapted: topower plants required tofrun at constant speed of Vrotation while the loadY demand on the turbine may vary. This condition arises WheneverV it is desired to operate a gas turbine power plant as a prime mover for electric alternators, synchronously connected to a constant frequency electrical network, or on ships in the propulsion with controllable pitch propellers.

Still another deficiency of the simple `Joule cycle is its inability to sustain overloads without increase of the maximum cycle temperature, which is altogether undesirable from the standpoint of strength and endurance of the turbine.

This-limitation constitutes a serious drawback to the application of continuous combustion turbines to transportation, for instance. in locomotives.

Ifl the load demand on a combustion turbine, operating according to the simple Joule cycle, is changed at constant speed, for example diminished, the maximum temperature of the cycle has to be. decreased by reducing the rate of the fuel consumption. The effect' of" this change'is to. cut down the heat drop1in the turbine, while the heat rise inthe compressor remains. approximately constant andv the difference of" these two energy conversions, the useful mechanical' energy, isthereby reduced to correspond to the decreased loadV demand.

These changes in the cycle bring about a rap-ld deterioration of the' cycle eciency, an undesirable characteristic ofthe simple Joule cycle, un'- less the other variable in the power output equation, viz., the' massv of the elastic fluid flowing through the cycle, be varied instead' of the useful heat' head; This latter consideration is indeed a sound one because while the change in the useful heat head at constant speed of rotation of the machines violates the laws ofdynamic similarityvof turbo machines and causes a deteriorationy of thermal eciency, the change inV the amount of mass of air operating within the cycle,

on' thev other hand, doesV not affect in any way the thermodynamic processes and laws of dynamic similarity of the machines. The thermal eiiicien'cy ofA the cycle remains therefore, constant regardless of how much mass or weight of air is operating in the cycle.

The-.disclosed invention provides a method of achieving` a complex .thermodynamic cycle of constant thermal eiciency under variable loads, byV functionally varying the mass.A density of the operati-ng. elastic. iluid of. the cyclewi-th the load andin proportion` to it; In essence, theinventionprovides. for a duall or twin Joule cycle; one, af` high pressure and constant compression ratio power cycle, called. byv us hereinafter the principal cycle, connected on: its low pressure side to the high: pressure" side of a second-,vlow pressureand variablel compression ratio cycle, called hereinafter the balancing cycle, based'on the atmospheric pressure and temperatur-e1 The: invention.. provides for a Variable power output of' the high pressurev principal. cycle with ,allf cycle temperatures, including the entry and exit temperatures of the: compressor as Wellk as the; entryan'df exit temperatures of thev turbine, held constant.. under all Aconditionsv ofv load de,- mand. the density of the elastic fluid vin this cycle being; determined' byv the controlling manipulatlonsl of' the.` lowV pressure,Y variable# compression ratio, balancing: cycle.` v A The.v constancy of the temperatures between which the: principal cycle operates at all loads means that the thermal eiiiciency of this' cycle is; also constant throughout the whole.y range of loads; The thermal efficiency ofthe balancing cycle isv a variable, beingv a. function of theV load on the' principal cycle. Since however, the power output of the balancing cycle is only a fraction of the output of-.the principal cycle, the net eiiect ofithis variation; on the. overall efficiency of .the complete power plant. is negligible'and the combined thermal efficiency of both cycles, when taken together, remains substantially constant at.- all loads;v f

Theimethod of. realization of this desired performance. consists of operating simultaneously and inter-dependently two sets of turbovmachines or other thermalprime movers. The smaller of the two machines. isy composed: by way of example, of an electric machine'ona common sha-ft with a low pressure compressor and with. a low pressure turbine.. v v

'I'his-'aggregate-, ucalled hereinafterthe balanct Ying;Y machine seitcanv rotate at variablespeed functionally determinedby the; external useful load produced. by the .principali cycle. The low 3 pressure compressor of the balancing machine set supplies fresh combustion air to the low pressure side of the larger, high pressure and preferably constant speed machine, generating externally useful power, and composed by way of example, of a principal turbine, a principal compressor and a power consumer, the whole aggregate called hereinafter the principal machine set, and the low pressure turbine of the balancing machine set obtains from the low pressure side of the principal cycle machine set a proportional amount of a mixture of hot air and burned gases for the propulsion of the balancing machine set. All combustion of fuel, either liquid, or gaseous, or powdered takes place at the highest pressure of the high pressure cycle, there being only one combustion heat generator in general, in the whole system, although more may be used, if so desired.

The rate of rotation of the balancing machine set determines the rate of supply of fresh air to the principal machine set and the pressure level and therefore, also the mass density of the mixture of air and gases, composing the elastic motive fluid with which the principal machine set is caused to operate.

The rate of supply of fresh air to the principal machine set also determines the rate of fuel consumption of and together with the level of the mass density of the elastic fluid, the power developed by the principal cycle. The operational coordination of the two machine sets, the balancing as well as the principal machine set, is accomplished by suitable controlling and regulating inter-connections between them; the method and means of regulation and control being the subject of the copending application Serial No. 301,224, filed July 28, 1952, although as will be explained further on, this regulation or balancing tends to become automatic, even without elaborate instrumentation.

Among the objects of this invention can be noted the desire to maintain a consistently high overall thermal eiiiciency of continuous combustion gas turbo plants at constant speed of rotation during all variations of useful load demand; this is of paramount importance in electric power generation where it is always necessary to maintain aconstant frequency of electric current, in phase with the rest of an electrical distributing system, regardless of the magnitude of the load. So far, the continuous combustion turbine has not been able to accomplish this without a major' Another object of the invention is to provide a y power plant in which high power overloads can be safely practiced without fear of endangering the strength of the essential components of the turbine of the principal machine set and rapidly deteriorating the durability of these parts by high temperatures; since the overload is manifested in the case of the disclosed combustion gas turbine power plant as an increase of torque and not as an increase of speed. it holds particular attraction for transportation, where the problem of starting large resistances into motion has always been somewhat of a diculty for all turbines.

Another object of the invention is to automatically maintain all determining temperatures of the principal cycle constant at all loads.

Another object of the invention is to provide an extremely compact and light weight power plant for very large powers, particularly suitable for transportation use, in locomotives and especially in ships; the invention makes possible gas turbine power plants of light weight and great compactness, uncommon even among lthe 'turbo 'machines.

Another object of the invention is to provide superior conditions for combustion in two respects, viz., by carrying out combustion at high pressures, even up to byway of example, approx. 100 atmospheres, of the motive elastic fluid, higher than ever reached before in continuous combustion gas turbines. The physico-chemical knowledge of combustion at high pressures recognizes burning at elevated pressures as superior to combustion at low pressure levels for reasons explainable by the kinetic theory of gases and also by test results. Furthermore, by maintaining combustion in an elastic fluid medium composed of a mixture of air and of burned gases at high temperature, such as carbon dioxyde and water vapor, the latter being a particularly potent catalyzer in the oxydizing reactions of fuel burning, the rate of combustion is known to be greater than when burning takes place in pure air.

Still another object of this invention is to reduce the size of the intake and exhaust ducts to the smallest possible minimum. It is preferable to mechanize the dual cycle with high pressure machines which, in general, can operate without heat recuperators and still produce high thermal cycle emciencies. In this connection reference is made to the copending application Serial No. 557,655, being led concurrently with this application and the copending applications Serial No. 179,028, filed August 12, 1950, and Serial No. 228,166, filed May 25, 1951, all dealing with the high compression ratio turbo machines, especially suitable for the embodiment of this invention. The principal cycle in its preferred embodiment using high compression ratio machines is capable of getting along with only one heat exchanger, operating always at relatively high pressures and never with the full amount of the total weight ow of the motive elastic fluid circulating in the ducting comprising the principal cycle circuit. The balancing cycle in its preferred embodiment incorporating the high compression ratio turbo machines according to the referenced copending applications, broadens the operational versatility of the principal cycle beyond any limit possible with low compression ratio machinery.

It is to be understood that although the use of high compression ratio machinery constitutes the preferred embodiment of the dual cycle invention, as described and shown in this specification, the invention can be also successfully practiced with low compression ratio machinery with the aid of heat recuperators which are not specifically described and shown here, but are described more fully in the application Serial No. 301,224, filed July 28, 1952. Still another principal object of the invention is to facilitate starting of large output, high pressure combustion turbines by novel electro-pneumatic means.

The novel features which are believed to be characteristic of the invention, both as to its organization and method of operation,` together with further objects and advantages thereof, will be better understood from the following description considered in connection with the accompanying drawings in which several embodiments of the invention are illustrated by way of an example. It is to be expressly understood, however, that the drawings are for the purpose of illustration and description only, and are not intended as a denition of the limits of the invention.

Fig. -l'is an entropy cycle of the pri-ncipalK-and auxiliary turbines ;VV

', Fig. 2- is a schematic diagram ofthe-power plant;V f I Figs;v 3 and 4 are schematic diagrams ofthe power plant illustrated -in Fig. 1 but having two themachines operating according t0 this dual cycle,.-inI Fig. 2. Both of;V these gures are so marked. at' various vdetermining points of the cycleA that'V corresponding locations in the two diagrams are designated by identical small lete ters of the alphabet. o

In Fig. 1 and Fig. 2, the points on the cycle shown on the T'S chart as well as on the schematic diagram of the circuit respectively, designated by letters e, f, y, c, demarcate the high pressure cycle called hereA the principal cycle, producing useful power. The operation of this cycle is carried out in succession by the compressor 5, drawing air at thermodynamic state'e, attemperature Te ,and pressure p1, and compressing it to a state f, at temperature Tf and pressure p2, raising the heat energy of air by an amount dened bythe temperature difference (Tf-Te). The compressedair enters thecombustion heat generator 2, in which burningfuel, liquid, gaseous or powdered, raises its temperature at substantially constant pressure pz to state g, at temperature Tg, thereby increasing the heat' energy of air by an amount defined by the temperature difference (Tg-Tf); The mixture of air and burned gases enters the turbine 1 from the heat generator 2 at temperature Tg and pressure.y pz and expands in it to thermodynamic state c, at temperature Tc and back to pressure p1, thereby converting an amount of heat energy, defined by the temperature difference (Tg-Tc), into mechanical energy, a portion of which drives the power consumer or converter, e. g., an electric alternator 8, mounted on a common shaft 9 with the air compressor 6 and gas turbine 1. After leaving the turbine at point c, the ow of the mixture of air and -burned gases, G in kgs/sec., is divided into two streams The largerY portion of' the circulating iiow, approx. SAG to %G, or from 60% to 85% of the exhaust gases appearing in the exhaust of the main turbine '1,by way of example, depending upon the maximum cycle temperature Tg, is ducted into the 'cooling heat exchanger lll, wherein the gaseous mixture is cooled to a thermodynamic state designated by point h, at temperature Th and at substantially constant pressure p1. The smaller portion of the flow vof the mixture, approx. lAlG to .1/G, of the total mass of the elastic motive fluid, circulating through the 'principal' machine set 6, '1, 8 or from 40% to of the exhaust gases appearing in the exhaust of the main turbine 1, is ducted by conduit l2 to the turbine `3, of the balancing machine set lf, 3, 4. In the balancing turbine 3, the mixture of air and burned gases is expanded from thermodynamic state c, to stated, at temperature Td and atmospheric pressure po, thereby converting an amount of heat energy, defined by temperature difference (Tc-Td), into -mechanical energy; the expanded gasesare discharged into the atmosphereby duct I4. The

balancing turbine 3 drives on a. common shaft: 5. the low pressure or balancing compressorv l' and an electric machine '4; The balancing Vcom-- pressor I draws air either in atmospheric or pre-compressed state, through intake duct"l'3.at temperature Ta and at ambient pressure po, corresponding to thermodynamic state designated by point a, and compresses it to pressure p1 and :temperature Tb, corresponding to thermodylnamc state designated by point b, on the low pressure isobar p1, of the principal cycle e,. La, c, increasing thereby the heat energy of the air by anamount defined by a temperature difference (Tt-Ta). lt is to be noted that by having a common isobar p1, the low pressure balancing cycle d, b, c, d, and the high pressure principal cycle e, y, c, are thereby mutually` interconnected physically and thermodynamically.

The compressed air arriving from the balanceing compressor l, is ducted by conduitv ll^,.to point l5 in the principal cycle circuit atwhi'ch the return conduit from the cooling heat exchanger lil is joined. Since the fresh air arriving into the principal cycle e, g, c,-is by way of example, at a higher temperature Tb, than the gaseous mixture cooled down to temperature Tn in the cooling heat exchanger Iii, a mixing process at substantially constant pressure pitakes place between the thermodynamic state h of the` gaseous mixture and state b of the incoming air, until an equilibrium temperature Te is reached substantially at constant pressure p1, before the entry to the principal compressor 6 at thermodynamic state designated by point c.

The principal cycle could operate equally well', as far as the principles of this invention are concerned, if the point designating Athe 'thermodynamic state b, at which the fresh air enters the' principal cycle, were located at a lower temperature than that corresponding to the point e, Fig. il, at which the high pressure compression begins. Such an arrangement would resultin a smaller heat exchanger li) than before 4with 'l"b Te, however at a cost of decrease of overall efficiency of the principal cycle. It may be expedient at times to favor a'slightlyv smaller heat exchanger lll and accept a lower overall cycle efficiency. rIvhe scope ofour invention is` therefore, not limited to a definite relation between temperature Tb and Th, but includes all feasible and practical temperature relations. v

The -amount of fresh air G1 kgs/sec., drawn in by the low pressure, balancing compressor l and delivered into the'principal cycle e, f, g,.c, need. not be more than is theoretically required for perfect combustion of fuel in the heat generator 2. This is possible only incur dual cycle, because at all times and under all conditions of load, there will always be present asuflicient amount of excess air in the heat generator 2v to maintain perfect andY completeburning of fuel. In order that no possibility may arise of supplyiing fuel at a greater rate than at which the fresh air is being replenished, it is preferable vtoset the value of G1 kgs/sec. at approx. G1:l.05 (the minimum amount of air required for combustion), although it may be a good practice to use much greater coefficient, say up to 1.25 in normal practice and even more under special conditions. It is preferable to keep the amount of fresh, renovating air entering the cycle, at the practical minimum in order-.to operate with as small a balancing` machine set as possible, for reasons of 7 sensitivity of control and in order to secure rapid response to regulating impulses.

. The overall efficiency of the dual cycle as described, can be expressed by the simplified relation:V

From this expression it can be seen that the first bracketed term is a constant for a given machine, because" it 'is a part of the specification of this invention that all the limit temperatures of the principal cycle must never change, while the second bracketed term is in general, a variable, because it is a part of the specification of this invention to vary the temperatures Tb and Td of the balancing cycle. It is clear that the second term should always be very small in order to maintain a substantially constant overall thermal efliciency mh, of the dual cycle. This is relatively easyvto satisfy, because the bracketed term is always small, while the value G1 kgs/sec. is deliberately kept low for reasons already noted.

The state of equilibrium of the dual cycle as described hereinabove, corresponds to a denite load demand on the principal power consumer or converter 8, and the whole dual cycle may be assumed balanced with respect to and in equilibrium with this load demand, all machines running in equilibrium, at constant speed and both, the balancing machine set as weil as the principal machine set operating at uniform, constant compression ratios.

If now the principal machine set B, '1, 8, is called upon, even suddenly, to deliver an increased power at constant speed of rotation to either an electric network or to a locomotive or to a controllable pitch propeller, the regulating and balancing devices subject of the copending application already referenced hereinabove, cause the balancing electric machine 4 to accelerate as an electric motor, the balancing compressor l and the turbine 3, from a rotational speed no, heretofore constant, to a higher rotational speed n1. At

the beginning of the acceleration, the rate of fuel supply to the heat generator 2 also begins to increase and simultaneously, the valve I8, located in the conduit I2 at entry to the turbine 3, is forced by governing and controlling means, to close, thereby blocking off either partially or completely, depending upon the severity of the load demand impulse, the flow of gaseous mixture from the principal cycle at thermodynamic state designated by point c, into the low pressure balancing turbine 3, during the period of acceleration of the balancing machine set I, 3, 4. This maneuver will, in eiect rapidly increase the pressure pi to a higher pressure pi, at the discharge point of the balancing compressor I, raising the temperature ofthe fresh air to Te, at point b', Fig. 1. Thus by speeding up the balancing machine set I, 3, 4, the principal cycle is not only being supplied with fresh replacing air at a greater rate than before, but the principal cycle itself is being displaced by this new set of conditions, into a new location on the T -S chart, in the direction of higher pressures, designated by position points e', f', g', c.

The highest cycle pressure thereby increases from y p2 to p'z, but the pressure ratio pz/p'i, remains constant and equal at all times, to the pressure ratio pz/pi, since the temperature ratios of any two temperatures of limiting points of the principal cycle e, f, g, c, remain always constant at all densities of the elastic motive fluid, at which the principal cycle may operate or in other words, regardless of the position of the principal cycle on the T-S chart. This inter-relation is the-result of dynamic similarity laws, that can be derived from the fundamental Laplaces relations:

7H Te p2 Therefore, the conditions of constant pressure ratio of the high pressure, principal cycle are automatically satisfied when the temperatures oi' that cycle are maintained constant at all points on the T-S chart. As soon as the equilibrium with the increased power demand of the energy consumer-or converter 8 has been established, valve I8 again fully opens, connecting the hot gas conduit -I2 to the entry of balancing turbine 3, resuming a continuous ilow of that amount G1 kgs/sec. of the mixture of air and burned gases that are being purged from the principal cycle e', f', g', c', by fresh air from the balancing compressor I at a new, higher pressure pi but a constant compression ratio pz/p'i, for the duration ofthe new load demand on the principal machine set.

It can be seen that the desired end, Viz., to attain a variation of the weight flow G kgs/sec. through the principal cycle, has been achieved by a change of the mass density of the working elastic fluid medium in the principal cycle. The limit of usefulness of this method is set only by the speed limit of the balancing machine set I, 3, 4, which as has been pointed out already, for reasons of small amount of fresh air that lhas to be replenished, will always be small in size and can therefore. not only accelerate and decelerate rapidly, but can also reach high speeds of rotation and consequently, high pressure ratios.

In the reverse direction, i. e., if there is a need for a decrease, even a sudden one, of external power on the principal machine set 6, 1, 8, the required regulating devices described in the copending application referenced hereinabove, diminish the amount of fuel that is being supplied to the lheat generator 2, at the same time automatically closing oi the air conduit Il, either completely or partially by the closure of valve I1 located near or on the stator of balancing compressor I, and simultaneously opening the exit of the balancing compressor I to the atmosphere.

During this controlling procedure, the gas valve I8 in conduit I2 remains fully open and the balancing turbine 3 keeps on delivering useful torque to the electric machine 4, operating it now as an electric generator, 'since the compressor I is unloaded except for its inherent losses. The pressure level of the common isobar p1 of the two cycles, mutually inter-connected, is quickly reduced, the mass density of the gaseous mixture in f 4the principal cycle e', f', g', c', is diminshed and the torque on the' principal machine set 6, 1, 8, is thereby decreased, without any change of the rotational speed of the principal machine set 6, 1, 8, because the heat rise determined by (Tf-Te) and the heat drop determined by (Tg-Tc) remain unchanged. As soon as the equilibrium with the reduced power demand of the energy consumer or converter 8, has been rre-established, valve I1 again fully opens, connecting the exit of the compressor l with the air conduit I I, re-establlshing `and decelerating impulses.

aY continuous flow of fresh, renovating air into the principal cycle e, f, g, c, at anew and lower `,pres-- :sure p1 but at constant compression ,ratio pif/p1 .for'the duration of the new load demand .on l,the

principal machine set.

Regardless in which direction the external power of the dual cycle has to be varied, either being increased or being decreased, as soon las the short time period of adjustment has beenpassed,

`the :balancing machine set I, 3, 4, settles down to a uniform speed of rotation either faster or slower than'before, but nevertheless constant for :a given condition of equilibrium, until the next load regulating signal may be received.

Closer study of the functioning of the balancing machine set I, 3, 4, reveals that lat all times except when accelerating, this machine will produce useful electrical energy in the electric machine 4, principally due to two favorable reasons, yone of which being Va slightly greater mass of gases flowing through the balancing turbine 3 than the amount of mass of fresh air which is being replenished by the lbalancing compressor I. This comes about due to the presence of constituents of the .burned fuel in the mass of the turbine gases, causing a slightly higher torque on the turbine shaft. The second and the main reason, is that the heat drop in the turbine 3, defined by the temperature difference (Ty-Td) at a higher` temperature level, is always greater than the heat rise in the ,compressor I, defined by the temperature :difference (Tb-Ta) at a lower temperature level, this being due to thephysical properties of lthe-air.

The `balancing of loads on the principal :machine set 6, 1, 8, and the regulating procedure zare, therefore, extremely .simple and rapid, due tothe vsmallness :and due also to the relatively low inertia of the balancing machine set l, 3, 4, ,and also due, in no small measure, t0 the functioning of the closing-off and by-passing operations of valves I'I and I8. It isnot necessary therefore, to employ an accumulating air receiver` forifresh air or a gas discharge valve to the atmosphere to :speed up regulation; obviously, by the load :bal-

plants lisginherently easier than of steam turbines,

because of the basic compressor load maintained by the combustion turbine and constituting a majOr portion of the total turbine output, which is always present under any external load demand, 'and also because of the simple continuity with which Vregulation can be practiced by thecontrol of the fuel supply, contrasted with the usual step regulation common in the steam turbines. However, should there arise a special case of the dual cycle application requiring sensitive balancing of extremely sharp and large load surges on the energy converter 8, the invention can be extended further, to include a parallel, secondary regulating or balancing machine as is shown in Fig. 3.

Referring to Fig. 3, it discloses two balancing machines I, 3, 4 and I', 2', 3' connected in -parallel. By splitting the balancing machine .into two smaller and identical units, of one .half the size ofthe principal unit, the mass moment ofinertia of the rotors may be assumed to be diminished approximately sixteen times, indicating for the same speed of rotation, a kinetic flywheel effect sixteen times smaller than before and fa correspondingly increased sensitivity tc'accelerating The dual balancing :sets I, 3 4, and I', .3', 4, vobtain the propulsive mixtures of hot air and burned gases from a common close-off valve I8 and by way of example, each turbine 3 and 3' receives one half vof the mass flow of lgases from conduit I2 and each compressor I and I' delivers one half of the fresh vreplenishing airthrough the .by-pass valve I'I yinto conduit I I and through it to the low 4pressureside of the principal cycle conduit.

The functioning of the twosmallba'lancing sets operating in parallel is analogous to the method described before for the cycle with only onebal .ancing set; fwith the exception that the .smaller machines, being ,considerably more responsive lto ,speed variation impulses, 4will rapidly answer any load variation signals.

The invention also provides for anovelmethod of starting of continuous combustion lgas turbines by means already contained iin the dual cycle arrangement for normal operation. The starting of the principal set 6, 1, 8fromfstandstillis accomplished according to conguration-shownin Fig. 2, by the complete closure ofthe vgasrelease conduit I2 byf-va'lve I8, preventing any youtflowof gases from the conduit I 2 and from the principal cycle circuit to the balancing turbine 3 yand'there- `upon to the atmosphere. Simultaneously, air ,conduit I I is closed oif by thevalve I Sandtheair flow from compressor I is directed by .said valve into -the conduit I B, entering 'the high pressure `side of the principal cycle ,at-point f, immediately before the heat generator, 4although anotherpoint of entry, e. g., :after the heat generator, could be selected on the vhigh pressure ,side ;of the principal cycle circuit and it is not, therefore, intended to limit our specification :to the fsingular connection shownrin thegures.

The electric machine 1I is Vrun zup, driving the balancing set compressor I and turbine 3 which as an idling machine without contributing to the driving vtorque due to the closure of valve I8. The compressor -I draws fresh air from .the .atmosphere and `aftercompressing it, drives with it :the

-principal turbine 'I of the Vprincipal machine set `l, 1, 8. The turbine 'I begins :to ,accelerate-under Ythe increasing pressure -of -ow of air from the compressor I. The air driving the turbine '1 iis ducted through the `heat exchanger -I- toV the high `pressure compressor `Ii, wherein it is lagain re-compressed, ducted to the combustion heat 4generator 2 and back to the vpoint g; whenthe predetermined pressure at `point ykhas been reached, fuel is caused to be introduced i-ntothe heat generator v2V ya-nd ignited, thereby :commencing combustion and a further acceleration of the principal turbine 'I, graduallyreaching the condition of autorotation of the` principal machine set :6, 1, 8. The principal machine lset henceforth operates -under its own power, -the starting process having been thereby accomplished and the valves I8 and I9 are automatically caused to be reset by gas pressure at point f, and by means not essential -to this specification but disclosedin copending application Serial No. 301,224, into their normal operating positions, allowing vfresh `air to enter the Yprincipal .cycle e, ,-f, g, c, on the low pressure isobar 'and letting the purging mixture of air and gases pass through the balancing turbine 3 to the atmosphere y Fig. -4 discloses an arrangement in which two auxiliary sets -I-3-4 and I-3'-4' are vconnected in series. This permits the operation of the main set 4Ii--l---ll at higher pressure than in Athe preceding cases, thus reducing its specific weight. The intermediate machine set 1I',

4', may operate either at constant speed or at a variable speed and it may be constructed in various size relationships with respect to' the principal machine set 6, 1, 8. The intermediate machine set l', 3', 4', receives compressed airirom the balancing set I, 3, 4, by conduit i i', re-compressesit and supplies it by conduit Il to the principal cycle circuit 6, 2, l, I0. Since with the high compression turbo machines described in the copending applications 557,655; 179,028; and 228,166, identied more fully before,referenced already hereinabove,it is possible to reach compression ratios of 10:1 inone rotor, it will be apparent that the principal machine set 6, 1, 8, can operate with pressures-oi the order of up to 100 atmospheres, making possible the realization of the greatest economically desirable outputs in very small turbo machines.

The dual cycle with an intermediate machine set can be extendedalso into its general configuration indicated in Fig. 4 by interrupted lines, including an intermediate cycle heat generator 2' and an intermediate cooling heat exchanger Hl' thereby completing the intermediate cycle circuit comprising machines and apparatus l', 2', 3', l', operating either to constant or variable temperature and therefore, according to the laws of dynamic similarity also at either constant or variable speed ofv rotation, according to the Achoice determined by the operational preferences. It will be apparent to those skilled in thermodynamics that a further extension or pyramiding of additional intermediate cycles, all operating in series and in addition, if so desired, in combination with machines operating in parallel.

Since the principal object of this invention is to maintain high and constant thermal efciency of gas turbines at variable load demand, the specification stresses the constancy of the rotational speed of the principal cycle. However, the disclosed cycle can be practiced also with the principal machine set 6, 1, 8, operating at variable speed, either in synchronisxn with the load demand or independent of it. According to the laws of dynamic similarity, the speed of rotation of a turbine and of a compressor is proportional to the square root of the absolute temperature ratio, (input temperature divided by output temperature) respectively, the speed variation on the principal machine set 6, 1, 8, requiring therefore, variation of temperature Tg in the heat generator 2 of the principal cycle circuit.

Although this operational method can be realized in conventional gas turbines as Well, it is limited there to the variation of speed as a function of the load demand only. According to this invention, the speed of the principal machine set 6, 1, 8, can be varied independently of the load demand, in fact the variation can be actually opposite in character. Thus by way of example, the principal machine set 6, l, 8, can be speeded up by the increase of temperature Tg in the heat generator 2, thereby increasing also the net output of the principal machine set as in a conventional gas turbine; Yor the density of the motive elastic iluid in the principal cycle circuit 6, 2, l, I0, can be decreased by slowing down the balancing machine set I, 3, 4, while the temperature in the heat generator Z is increased, thereby either maintaining constant power outputonpower consumer 8 with increased speed or even a decreased power output on said power consumer with increased speed. These operational features and advantages are inherently characteristic of the disclosed cycle and are especially sought after in transportation propulsion, e. g., for locomotive drive'sfusing mechanical transmissions, making `possible attainment of high torques at low speeds and conversely, of low torques'at high speeds, neither one of these characteristics having as yet been realized by any known turbine prime movers.

What is claimed is:

l. The method of increasing the rate of flow of a working fluid through a first and principal compressor-turbine set 4in response to an increase in a load connected to said iirst set from a first, small load to a second greater load, by increasing the mass-density of the fluid furnished to said rst set by acompressor of a second, balancing compressor-turbine-electric machine set, said method including'the steps of, as long as said iirst'load remains constant, precompressing said fluid in said second compressor to a pressure '231; conveying the precompressed uid to said first compressor; compressing, in said rst compressor, said precompressed iuid from pressure p1 to pressure p2 .for obtaining a compressed fluid; mixing and burning fuel in said compressed fluid for producing an exothermic gaseous reaction thereby producing the products of combustion having a temperature Tg and pressure 02, expanding said products of combustion through said firstturbine to a pressure not lower than p1; expanding from 40% to 15% of the exhaust gases leaving said rst turbine still further through said second turbine; driving said second compressor and said machine as a generator from said second turbine; cooling and then mixing the remaining 60% to 85% of said exhaust gases with said precompressed Huid; conveying the mixture of the precompressed fluid and exhaust gases to the input of said i'lrst compressor; and increasing the mass-density of the iiuid, of the products of combustion and of the exhaust gases, respectively, owing through said first and second sets, in response to an increase in said first load to said second load by iirst operating said electric machine as a motor at ahigher speed than the prior speed of said machine when operated as a generator during said first load, thereby accelerating said second compressor for compressing said fluid to a higher pressure 101'; increasing the amount of the fuel supplied for said exothermic reaction to the extent necessary for maintaining the temperature Tg constant; returning all the exhaust gases to the input of said first compressor during the transition period from the iirst load to the second load; mixing the precompressed uid and the exhaust'gases prior to their entry into said first compressor; compressing the mixed fluid and the exhaust gases from pressure p1 to pressure p2' With the compression ratio of said first compressor remaining constant; and, upon establishing the power equilibrium between said second load and the power delivered by said first turbine, redirecting the 60% to 85% of the exhaust'gases back to said rst compressor, and 40% to 15% of the exhaust gases to said second turbine while maintaining said compression. ratio of the first compressor constant; whereby said second turbine again drivesV said second compressor and said electric machine as a generator as long as the increased load remains constant.

2. The method as dened in claim l which also includes the steps of stopping the flow of the precompressed fluid from said second compressor to said first compressor during the transition period from the second load to a decreased load, and restoring said ow upon establishing the power equilibrium between the decreased load and the power `producedby said iiist turbine;..de creasing the amount of ffuel -to'maintain temperature Tg constant, and reducing the coni-pression ratio of the second compressor in proportion to the decrease in said load by lreducing its :angular velocity Whileniaintaining the compression ratio of the iirst compressor substantially constant.

3. The method of varying the rateof flow of a working fluid through a iirst 'and principal compressor-turbine set in response to a variation in aload connected to said first .set 'by varying the mass-density of the iiuid furnished to said rst set by a compressor of a second, balancing compressor-turbine-electric 'machine set, lsaid method including the steps .of precompressing said fluid in said second compressor to a pressure 131'; conveying the precompressed iiuid to said ist compressor; compressing, in said vfirst -compressor, said precompressed fluid from pressure pi to vpressure p2 for obtaining a vcoin-pressed fluid; mixing and Aburning fuel in -saijd compressed fluid for producing an exothermic vgaseous reaction, thereby producing theproduc-ts of combustion having a tempera-ture T-g 4and pressure fpz"; 'expanding said products `of ncombustion 'through said first turbine to a pressure not lower -thanfpi expanding from 40% to 15% of the exhaust gases leaving'said iirst turbine vsti-ll further-'through 'said-second turbine as vlong as said Iload remains substantially constant; driving said second 'comf pressor and said 'machine as Va generator from said Isecond turbine; Icooling and then returning the remaining 60% to 85% of said exhaust gases to 'the input of said first compressor; fand vdecreasing `the mass-density of the nuid, products of combustion 'and exhaust gases, flowing, respectively, through said first land second sets, in re,- sponse to a decrease in `said `load-by iirst vreducing the amount of the fuel `supplied for said/exothermic reaction; discharging the iiu'id output of said second compressor into an ambient *fluid during the transition period from the original load to the decreased load until pi' is decreased Vto p1 and p2 is decreased to pz, said decrease in 4. The method as defined in 'claim 3, Whichalso includes the step of 'decreasing the amount of the fuel supplied `for Ysaid exothermic reaction only to the extent necessary for 'maintaining TTg constant..

v5. The method of varying `the rate of .flow of a working fluid through a iirst and principal compressor-turbine set in response vto Va variation in a load connected to said viirst 'set "by varying the mass-densityfof the fluid furnished to said :iii'st set by la compressor of a second, balancing compressor-turbine set, said method including the steps of precompressing said uid in said second compressor to a pressure pi; conveying .the-precompressed fluid to said first compressor.; -compressing, in said first compressor, said precompressed fluid from pressure p1 to a pressure p2 for obtaining a compressed iiuid; mixing and burning fuel in said compressed fluid for producing an exothermic gaseous reaction, thereby producing the products of combustion having a temperature Tg and pressure p2; expanding said products of combustion through said first turbine to a pressure not lower than p1; expanding, at least that portion of the exhaust gases which is necessary for maintaining stoichiometric combustion of said fuel Within .said compressed uid, still further through said second turbinel as lon-g as said load remains constant; cooling andthen returning the remaining major portion of .said exhaust gases .to the input of saidarst compressor; and increasing the .mass-density. of the fluid Aand of the products of .combustion .in re'-v sponse to an increase in the `load connected to said first turbine by first increasing the .amount of `lfuel furnished vfor said `exothermic reaction for maintaining Tg constant; removing, during the transition periodffrom the `lighter load to the heavier load, the external load carried. 'by said second turbine; furnishing an external power, other than said second turbine, rfor driving said second compressor at a lhigher :speed than itsspeed at lthe lighter load, saidiincrease in speed increasing pressure pi to pi; raising pressure vp2 to p2 by directing, during said-transition period, the entire exhaust gases to thefine put of said rcompressor and by increasing-fthe input pressure into the second'compressor from zu to pi'.; and, upon establishingthe power equilibrium between the increased load yandthe `power delivered by said iirs-t turbine, redirecting f the ilow of the same at least stoichiometric portion of the exhaust gases vto said; second turbine .for restoring the function of said -second-.turbineias a prime mover for said second lcompressor and said external load. r

6. The .method of varying the rate of iiow of a Working fluid through a iirst compressorturbine set in response to a variation in ia Aload connected to said iirst set by VVvarying the massdensity of the nuid furnished tor-said rstfset by a compressor of ya second, 'balanci-ngcom` presser-turbine set, said 'method including Ithe steps `of precompressing said :fluid in. saidy Asec-f ond compressor; conveying the precompressed iiuid yto said `first compressor; compressing said precompressed fluid in said first compressor for obtaining `a compressed flu-id; mixingandburning fuel in said compressed fluid for producing an exother-mic gaseous reaction with the rproducts. of combustion having -a tempera-ture "15g: expanding said products Yof :combustion :through said first turbine for driving said first turbine iat constant angular velocity; vexpanding from-40% to 15% of the -exhaustgasesy leaving 4said firs-tritur-A bine, still further through said second turbine; driving said second compressor from said second turbine; Acooling andv then, as long Aas said ,load remains constant, returning the remaining pore tion of .said exhaust .gases to the input of vsaid first compressor by first mixing said remaining exhaust gases with the compressed ,-iiuid .leaving said lfirst compressor; :and .increasing the kmass-'- density auf 'the products of combustion, "owing through said first tui-.bine by momentarily 4'stopping `theflovv` of the exhaust gases to said sec-- ond "turbine "during the transition period 'f rom the smaller Aload to a larger-load, and directing jall exhaust gases to said rst compressor;4 increa ing 'theamount of 'the`.fuel Afor lsaid, exotlier,Y reaction for maintaining 'Tg .constant ydriving said second compressor from an external source of power at a greater speed than its speed during the smaller load until said greater speed and the increased amount of fuel create a mass-density of the products of combustion to drive said iirst turbine at said constant angular velocity in spite of the increase in said load, and then again restoring the now of the same 40% to 15% portion of said exhaust gases to said second turbine for driving said second compressor again from said second turbine.

7.r 'I'he method as delined in claim 6 which also includes the steps of discharging the precompressed fluid into an ambient duid and reducing the amount of fuel for said exothermic reaction during the transition period from said larger load to said smaller load, and then again discharging said precompre'ssed uid and said exhaust gases into said first compressor upon reduction of the mass-density of the products of combustion, flowing through said rst turbine, to a lower level, corresponding to the reduction in said load. 8. A method of starting a first compressorturbine set with the aidof a compressor of a second compressor-turbine set, said rst and second compressors, and said rst turbine, being connected to a combustion heat generator, said method including the steps of applying an external power to said second set for driving said 'second set, precompressing an ambient fluid in said second compressor, discharging the entire precompressed fluid directly into said combustion heat generator, feeding into and burning fuel Within said pre-compressed iiuid in said combustion heat generator for producing products of combustion, discharging all of said products of combustion into said first turbine, expanding all l of said products of combustion through said first turbine whereby said products of combustion appear as exhaust gases on the output side of said first turbine, cooling all of said exhaust gases and then conveying al1 of the cooled exhaust gases to the input side of said rst compressor, recompressing the cooled exhaust gases in said first compressor while driving it from said first turbine, and discharging the recompressed exhaust gases from said first compressor directly back to said combustion heat generator.

9. The method as deiined in claim 8, which, upon resumption of a normal speed by said first set, also includes the steps of discharging the entire precompressed fluid into the input side of said first compressor, discharging from to 15% of the exhaust gases to the input side of said second turbine for normally driving said second compressor from said turbine, and discharging the remaining 70% to 85% of the exhaust gases to the input side of said first compressor.

10. The method of operating a rst compressor-turbine set with the aid of a second compressor-turbine set and a combustion heat generator interconnecting the compressor and the turbine of the iirst set, said method including the steps of driving said second compressor from said second turbine for precompressing an ambient fluid from pressure po to pressure p1, conveying the precompressed fluid to said rst compressor and compressing it to pressure p2, discharging said compressed fluid into said combustion heat generator,. feeding into and burning fuel within said compressed fluid, thereby producing products of combustion, expanding said products through said first turbine for driving said first compressor and an external load,

said products of combustion appearing as exhaust gases at the exhaust side of said first turbine, expanding still further a rst portion of the exhaust gases through said second turbine for driving said second compressor, cooling and then combining and mixing the second and remaining portion of the exhaust gases with said precompressed fluid, whereby said first compressor receives mixed gases containing said compressed fluid and said remaining portion of said exhaust gases, and shifting the operation of said first set to a higher pressure cycle with the increase in said load by increasing p1 to p1 and to pz', While maintaining the compression ratio by increasing the angular speed of said second compressor, increasing the amount of fuel to the extent required for maintaining the temperature of said products of combustion constant irrespective of the change in said load, and by increasing the second portion of the exhaust gases discharged into said precompressed fluid only during the transition period from the previous load to the increased load, said increase being a function of the increase in said load, and of the rate of increase in said load, the maximum of said second portion being of said exhaust gases.

11. The method as delined in claim l0 which also includes the step of returning the operation of said second set to a lower pressure cycle by discharging a portion of the output of said second compressor into an ambient fluid during the transition period from a large external load to a small external load, the discharged portion being a function of the decrease in said load, and the rate of decrease of said load, the maximum of said portion being 100% of said precompressed fluid.

VLADIMIR H. PAVIECKA. FREDERICK DALLENBACH.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,766,886 Elling June 24, 1930 2,095,991 Lyholsm Oct. 19, 1937 2,172,910 Keller Sept. 12, 1939 2,245,954 Anxionnaz June 17, 1941 2,268,270 Traupel Dec. 30, 1941 2,298,663 Traupel Oct. 13, 1942 2,303,381 New Dec. 1, 1942 2,318,905 Traupel May 11, 1943 2,365,551 Hermitte Dec. 19, 1944 2,407,166 Kreitner Sept. 3, 1946 FOREIGN PATENTS Number Country Date 228,290 Switzerland Nov. 16, 1943 378,229 Italy Jan. 25, 1940 

